EP0023467B1 - Brennstoffeinspritzpumpe - Google Patents

Brennstoffeinspritzpumpe Download PDF

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Publication number
EP0023467B1
EP0023467B1 EP80630026A EP80630026A EP0023467B1 EP 0023467 B1 EP0023467 B1 EP 0023467B1 EP 80630026 A EP80630026 A EP 80630026A EP 80630026 A EP80630026 A EP 80630026A EP 0023467 B1 EP0023467 B1 EP 0023467B1
Authority
EP
European Patent Office
Prior art keywords
distributor
pumping
fuel injection
injection pump
liquid fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP80630026A
Other languages
English (en)
French (fr)
Other versions
EP0023467A1 (de
Inventor
Charles Wade Davis
Charles James Donahue
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Stanadyne LLC
Original Assignee
Stanadyne LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Stanadyne LLC filed Critical Stanadyne LLC
Publication of EP0023467A1 publication Critical patent/EP0023467A1/de
Application granted granted Critical
Publication of EP0023467B1 publication Critical patent/EP0023467B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis

Definitions

  • such pumping plungers are mounted on a common diametral axis and the cooperating cam lobes are also provided in pairs disposed 180° apart to actuate the plungers inwardly along the common axis so that side loading is not applied to the rotary distributor.
  • the cooperating cam lobes and the pairs of pumping plungers cannot be readily placed on a common diametral axis.
  • Fig. 1 is a front elevation view, partly in section and partly broken away, of a fuel injection pump embodying the present invention and suited for use with an uneven firing V-6 engine;
  • the fuel pump 10 exemplifying the present invention is shown to be of a type for supplying measured charges of fuel to the several fuel injection nozzles of an associated internal combustion engine.
  • the pump has an axial bore 12 in which the rotary distributor 14 is journaled.
  • a vane-type transfer or low pressure supply pump 16 is mounted by the rotor to be driven thereby and receives fuel from a reservoir (not shown) through a pump inlet 18 and delivers fuel under pressure to a metering valve 20.
  • a pressure regulating valve (not shown) is mounted in a bypass passage between the outlet 22 and the inlet 18 of the transfer pump 16 to regulate the output pressure of the transfer pump and provide a pressure correlated with engine speed.
  • a high pressure charge pump which comprises a pair of plungers 24 slidably mounted in radial bores of the rotor, receives metered fuel from the metering valve through a diagonal passage 26 in the rotor adapted for sequential registration with ports 28 communicating with passage 30 down-stream of the metering valve 20 as the rotor is rotated.
  • a generally circular cam ring 32 Surrounding the rotor in the plane of revolution of the plungers 24 is a generally circular cam ring 32 having a plurality of inwardly extending cam lobes 34 which are adapted to actuate the plungers 24 inwardly simultaneously to pressurize the charge of fuel therebetween.
  • the rollers 36 and roller shoes 38 are disposed between the plungers 24 and the cam ring 32 so that the rollers act as cam followers for translating the cam contour into recipro- cable movement of the plungers.
  • cam ring 32 which may be angularly adjusted by a conventional timing piston 50 connected to the cam ring 32 by a connector 52 to shift the angular position of the cam ring as desired.
  • the pair of pumping plungers 24 and their associated rollers 36 and shoes 38 are angularly spaced on axes 120° apart as shown in Fig. 3.
  • the cam ring has a first set of three cam lobes 34 which are also angularly spaced 120° apart for the simultaneous actuation of the two pumping plungers to deliver charges of fuel to the three cylinders of one of the banks of the V-6 engine.
  • the cam ring 32 is also provided with a second set of three cam lobes 34a which are angularly displaced 120° from each other to deliver charges of fuel to the three cylinders of the other bank of the engine.
  • inlet passage 26 which terminates in a port in the form of an enlarged chamber or pad 58 communicates with axial passage 42 of the rotary distributor 14.
  • the pressurized fuel in inlet passage 26 creates a hydraulic force between the rotary distributor and the bore 12 in which it is journaled and, according to the invention, the port of inlet passage 26 is angularly oriented so that this hydraulic force is aligned with radial vector A, but acts in the opposite direction.
  • inlet passage 26 does not register with an inlet port 28 during pumping strokes when the rollers engage the cam lobes.
  • inlet passages 26a do not register with inlet ports 28a during pumping strokes. In each embodiment, however, the inlet ports register with the inlet passages each time that the rollers 36 are disposed between adjacent pairs of cam lobes in order to charge the pump.
  • the variant shown in Figs. 6 and 7 illustrates the use of the invention with respect to a five-cylinder even firing engine.
  • a single inlet passage 26 is used.
  • the cam lobes 34b of the cam ring 32a and the inlet ports 28b are evenly spaced 72° apart and the inlet ports 28b are angularly located so as to register with inlet passage 26 when the rollers 36 are between adjacent cam lobes in order to charge the pump.
  • the ports 28b are out of registry with the inlet passage 26 during the pumping stroke of the pumping plungers 24 as shown in Fig. 7.
  • the pumping plungers 24, as shown in Fig. 6, are preferably angularly displaced 144° from each other to produce the minimum side loading on the rotary distributor 14a.
  • this invention permits the use of a pair of pumping plungers not located on a common diametral axis without the use of any additional parts by creating a hydraulic counterbalancing force which automatically adjusts in accordance with the pressure levels generated in the charge pump at different pumping speeds and pumping rates.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Claims (8)

1. Flüssigkraftstoffeinspritzpumpe mit einer Längsbohrung (12), einem in der Bohrung gelagerten Drehverteiler (14), welcher Drehverteiler mit zwei im wesentlichen radialen miteinander in Verbindung stehenden, nicht-koaxialen Bohrungen versehen ist, zwei Pumpenkolben (24), die in den nicht-koaxialen Bohrungen gleitend geführt sind zur Bildung einer Pumpenkammer zwischen diesen Kolben, und einem Nockenring (32), der um die Drehachse des Verteilers herum angeordnet ist und Nockenbuckel (34, 34a, 34b) aufweist, um während der Drehbewegung des Verteilers den Pumpenkolben gleichzeitig eine nach innen gerichtete Bewegung zu erteilen, wobei zwischen dem Verteiler und der Längsbohrung eine Kammereinrichtung (58, 58a) gebildet ist und eine Kanaleinrichtung (26, 26a) in dem Verteiler eine kontinuierliche Verbindung zwischen der Kammereinrichtung und der Pumpenkammer bildet, dadurch gekenzeichnet, dass die Kammereinrichtung (58, 58a) in Winkelrichtung angeordnet ist zur Ausübung einer hydraulischen Kraft auf den Verteiler (14), welche Kraft im wesentlichen mit dem radialvektor der Seitenbelastung zusammenfällt, die während dem Pumphub der Pumpenkolben (24) auf den Verteiler ausgeübt wird, jedoch entgegengesetzt zu diesem gerichtet ist.
2. Flüssigkraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Kammereinrichtung zwei Kammern (58a) aufweist, dass zwei Einlasskanäle (26a) die Kammern (58a) mit der Pumpenkammer verbinden, wobei die Kammern (58a) auf gegenüberliegenden Seiten des Radialvektors der Seitenbelastung des Verteilers (14) angeordnet sind.
3. Flüssigkraftsoffeinspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die beiden Kammern (58a) und Einlasskanäle (26a) winkelsymmetrisch in bezug auf den Radialvektor sind.
4. Flüssigkraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Kammereinrichtung eine Ausgleichskammer umfasst, welche in einem Druckraum endet, der mit dem Radialvektor radial ausgerichtet ist.
5. Flüssigkraftsoffeinspritzpumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass eine Ausgleichsbohrung (54) in dem Verteiler (14) angeordnet ist, welche Ausgleichsbohrung (54) mit dem Vektor radial ausgerichtet ist, sich jedoch in axialem Abstand von den Einlasskalälen (26a) befindet.
6. Flüssigkraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Kammereinrichtung (58, 58a) eine Abmessung aufweist, um eine hydraulische Gegenkraft zu erzeugen, welche die Seitenbelastung im wesentlichen ausgleicht.
7. Flüssigkraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Nockenring (37) fünf Nockenbuckel (34b) aufweist, welche gleichwinklig um seinen inneren Umfang angeordnet sind, und dass zwei abwechselnde Nockenbuckel die Pumpenkolben (24) betätigen.
8. Flüssigkraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Nockenring (32) zwei Sätze gleichwinklig in Abstand voneinander angeordnete Nockenbuckel (34, 34a) an seinem inneren Umfange aufweist, wobei der Winkelabstand benachbarter Nickenbuckel des Nockenringes ungleichförmig ist, und dass Nickenbuckelpaare eines jeden Satzes abwechselnd die Pumpenkolben (24) betätigen.
EP80630026A 1979-07-31 1980-07-14 Brennstoffeinspritzpumpe Expired EP0023467B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US62356 1979-07-31
US06/062,356 US4255097A (en) 1979-07-31 1979-07-31 Fuel injection pump

Publications (2)

Publication Number Publication Date
EP0023467A1 EP0023467A1 (de) 1981-02-04
EP0023467B1 true EP0023467B1 (de) 1983-07-27

Family

ID=22041933

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80630026A Expired EP0023467B1 (de) 1979-07-31 1980-07-14 Brennstoffeinspritzpumpe

Country Status (10)

Country Link
US (1) US4255097A (de)
EP (1) EP0023467B1 (de)
JP (1) JPS5623556A (de)
AR (1) AR221656A1 (de)
AU (1) AU535860B2 (de)
BR (1) BR8004702A (de)
CA (1) CA1133341A (de)
DE (1) DE3064401D1 (de)
ES (1) ES493844A0 (de)
IN (1) IN152494B (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4675826A (en) * 1984-08-06 1987-06-23 Granco-Clark, Inc. Temperature control system
DE3437973A1 (de) * 1984-10-17 1986-04-17 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE19542952A1 (de) * 1995-11-18 1997-05-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US20060159572A1 (en) * 2005-01-18 2006-07-20 Malcolm Higgins Pilot injection pump
DE102017222546A1 (de) * 2017-12-13 2019-06-13 Robert Bosch Gmbh Kolbenpumpe zur Förderung von Druckmittel in einem Druckmittelkreis

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT200853B (de) * 1956-05-30 1958-11-25 Friedmann & Maier Ag Einspritzpumpe
FR1384096A (fr) * 1963-11-21 1965-01-04 Sigma Perfectionnements apportés aux pompes d'injection à distributeur pour moteurs à cinq cylindres
US3267761A (en) * 1964-05-08 1966-08-23 Case Co J I Power control mechanism for a variable ratio drive
GB1227332A (de) * 1967-05-23 1971-04-07
DE2102761C3 (de) * 1971-01-21 1974-11-07 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe
DE2113396A1 (de) * 1971-03-19 1972-09-21 Teves Gmbh Alfred Radialkolbenpumpe
DE2349332A1 (de) * 1973-10-01 1975-04-03 Wepuko Hydraulik Gmbh Innenbeaufschlagte radialkolbenpumpe
US3883270A (en) * 1974-03-22 1975-05-13 Stanadyne Inc Fuel pump
FR2367197A1 (fr) * 1976-10-11 1978-05-05 Roto Diesel Sa Perfectionnements aux pompes d'injection de combustible pour moteurs a combustion interne
GB1592172A (en) * 1977-01-28 1981-07-01 Lucas Industries Ltd Fuel pumping apparatus

Also Published As

Publication number Publication date
JPS5623556A (en) 1981-03-05
DE3064401D1 (en) 1983-09-01
AU535860B2 (en) 1984-04-05
JPH0231223B2 (de) 1990-07-12
AU6092180A (en) 1981-02-05
EP0023467A1 (de) 1981-02-04
IN152494B (de) 1984-01-28
BR8004702A (pt) 1981-02-10
ES8103283A1 (es) 1981-02-16
ES493844A0 (es) 1981-02-16
CA1133341A (en) 1982-10-12
US4255097A (en) 1981-03-10
AR221656A1 (es) 1981-02-27

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